Transmission



D. w. KELBEL TRANSMISSION Aug. 5, 1952 2 SHEETS -SHEET 1 Filed July 17,1947 fnveni or" .Panczlcl Zfl Kelel D. w. KELBEL Aug. 5, 1952TRANSMISSION 2 SHEETS-SHEET 2 Filed July 17, 1947 fizv'erzfor Donald ZZZff E n Mm @Nq m Patented Aug. 5, 1952 2,605,652v TRANSMISSION Donald W.Kclbel, MuncieJnd assignor to Borg- Warner Corporation, Chicago, 111., acorporation of Illinois ApplicationJuly 17, 1947, Serial No. 761,615

- My invention relates to transmissions for automotive vehiclesand moreparticularly-to-such transmissions having hydrodynamic torque convertersfor completing the drive.

It is an object of my invention to provide an 2 Claims. (Cl. 74=763)improved transmission of this type which in-f eludes gearing in serieswith a hydrodynamic coupling unit giving threediiferent forward speedratios. It is a further object to provide-such gearing which is compact,is easily controlled, and is simple in nature. It is contemplated thatthis gearing shall be of the planetary type.

It is a further object of the invention to provide such gearingconnected in series with a torque converter which is controlled by aplurality of frictionally engaging elements, such as friction clutchesand friction brakes, and it is also an object to provide such gearingwhich provides three forward speeds and a; drive in reverse with aminimum number of such frictionally engaging elements.

The invention consists of the novel constructions, arrangements, anddevices to be hereinafter described and claimed for carrying out 'theabove-stated objects and such other objects as will appear from thefollowing description of a certain preferred embodiment illustrated inthe accompanying drawings, wherein:

Fig. 1 is a longitudinal sectional View of a transmission embodying theprinciples of the invention, and

-'Fig. 2 is a schematic View of the transmission illustrated in Fig. 1.r r

Like characters of reference designate like parts in the several views.v I

Referring now to the drawings, the illustrated transmission comprises ingeneral an input shaft ||l, an output shaft M, an intermediate shaft [2,and a second intermediate shaft [3; The transmission is intended to beuseful particularly with automotive 'vehicles, and the input shaft Illis intended to be connected with a driving engine (not shown) of such avehicle, and the output shaft H is intended to be connected with thedrive wheels (not shown) of the vehicle.

The input shaft Ill is connected to drive a hydrodynamic torqueconverter M by means ;of .a planetary speed-up gear set l5. The shaft I2is driven by the torque converter and is adapted to drive a planetarygear set it. A pair of friction clutches I! and I8 are'pro-vided forselectively connecting the shaft l2 with different elements of the gearset it, and friction brakes I9 and 20 are providedfor braking certainelements of the gear set to provide reaction members in the gear set. 1

the intermediate shaft l2.

drives a flywheel 2|, and the-flywheel is connectedto the speed-upgearing |5'by means of a vibration dampener 22. The vibration dampenercomprises springs 23 acting The input shaft In between opposite parts 24and 25, and the type of dampener shown is well known in the art and,therefore, need not be described morein detail.

The planetary gear set l5 comprises a sun gear 26, a ring gear 21, andapair of planet gears-28 and 29. -The planet gears 23 and 29 are in meshwitheach other, and the gear 29 is also in mesh with the ring gear 21,and the gear 28 is also in mesh with the gear 26. .The planet gears 28andZSl are rotatably mounted in a planetgear carrier 30. .Thering gear21 -isconnected .to be driven by the vibration dampener 22 and the sungear 26 is "splined to The planet gear 1 carrier '36 is connected withthe torque converter planet gear pinions 1 mesh with the "ring gear 39,and

l,as will hereinafter'be. described more in detail. The torqueconverter. i l comprisesan impeller l or driving element 3|, a rotor ordriven element 32, and a. stator 'or reaction element '33.; The impeller3| is connected to the planetgear ,carr'iertll. of the; gear set 15,and'the rotor 32 islsplinejd tothe shaft 12. The stator 33 is rotatablydisposed on a central hub 34 which i is fixed with respect to the casing35 of the transmission. A one-way roller brake 36 is provided betweenthehub 34 and the stator 33 for allowing the stator to rotate only in theforward di rection for purposes well known in the transmission art. Theintermediate shaft I2 is ro- .tatably disposed with respect to thecasing 35 by means of a in the drive shaft ID as bearing 31, and thisshaft is piloted shown. 'The impeller means .of a bearing 38, as. willbe noted. -;The planet gear set It comprises a ringv gear 33 connectedwith, the output shaft II and, as will be noted, the ring gear and theoutputjshaft are rotatably disposed within the casing 35 by 'means ofabearing 40. The gear seti'ncludes 4| 1splined-to the second intermediateshaft |3' which, as will be noted, is pilotedwithin'the shafts l| and|2.-. A pair of 42 and 43 in mesh with each other are provided, and'thegear 42 is also in v} 4 v the gear A3 is also inmesh with the sun gear4|. The gears 42 and-E3 arerotatably mounted in a planetary also a sungear gearcarrier 44 which is rotatably disposed with extends forwardlyof the transmission with respect to that portion-of the gear in meshwith the gear 43, and a sun gear 45 is provided in mesh with the gearportion 42a. The sun gear 45 is splined on a shaft 46 which is rotatablydisposed on the intermediate shaft I3. It is to be noted that thecarrier 44 is rotatably mounted with respect to the shaft 46 by means ofan intermediate collar 47, and this collar is supported by a portion 35aof the casing 35.

The friction clutch I1 is provided for drivingly connecting the shaft I3with the shaft I2 and comprises a plurality of friction plates 48 and49. The clutch comprises an outer shell 59 to which the plates 48 aresplined and an inner shell I to which the plates 49 are splined. Theouter shell 59 is splined to the shaft I2 and the inner shell 5I issplined to the shaft I3. The outer shell 59 is provided with an annularcavity 52 in which a piston '53 of the same general shape is disposed.The piston is adapted to be moved by fluid under pressure appliedthereto, as will be henceforth more fully described, so as to move thefriction plates 48 and 49 together for engaging the clutch II. A spring54 is provided between the piston and a collar 55 fixed to the shell 59,and this spring functions to move the piston 53 into its retractedposition, in which it is shown in the drawings.

The clutch I 8 is generally similar to the clutch I I and comprises anouter shell 56, an inner shell 51, clutch plates 48 and 49 splinedrespectively to the outer and inner shells, a fluid pressureoperatedpiston 58, a spring 59 acting on the fluid piston, and a retainer collar69 for the spring. The outer shell 56 is splined to the shaft 46 and theinner shell 51 fits on and isrotatably disposed with respect to theshaft I3. A bridging member BI is provided for connecting the outershell 59 of the friction clutch I! with the inner shell 51 of thefriction clutch I8 so that these two parts rotate together and thefriction plates 48 of the clutch I! and the friction plates 49 of theclutch I8 act as the driving plates in the respective clutches.

(as from the output shaft I I, as will be described in more detailhereinafter), the clutch engages and rotates the carrier in the forwarddirection.

The friction brake I9 comprises a brake band 62 which act on the outershell 56 of the clutch I8, thereby braking the hollow shaft 46 and thesun gear 4'5. The brake I9 may be actuated by any suitable means, suchas by a fluid pressure actuator 63 of any suitable construction. Thebrake 29 comprises a brake band 64 acting on a drum 65 which is providedon the planet gear carrier 44. This brake band may also be actuated by afluid pressure actuator 66 of any suitable construction.

The transmission is provided with two fluid pressure pumps 67 and 69'which may be of the gear or any other suitable type. The pump 61 isdriven by gears 69 and I9,.as shown. The gear 69 is fixed with respectto the impeller 3I of the converter I4 and meshes with the gear I9 whichis connected directly to the pump 51. The inlet II of the, pump 61extends into the lower portion 35b of the transmission casing 35. Sincethe gear 69 rotates with the impeller 3I of the converter I4, it isapparent that this pump is driven by the input shaft I9. The pump 68comprises a gear I2 which is splined to the output shaft II, and thispump thus is driven by this shaft. The pumps may be connected with anysuitable hydraulic system (not shown) for actuating the clutches I1 andI8 and the brakes I9 and 29.

A one-way roller clutch I3 is provided between the intermediate shaft I2and the planet gear carrier 39 of the gear set I5. This roller clutch isso constructed that when the carrier 30 A fluid conduit 14 is providedin the casing 35 for supplying the torque converter I4 with fluid underpressure. Various bearing portions of the intermediate shaft I3,indicated at I3a, I 3b, I 30, and I3d, are lubricated by fluid which isderived from the torque converter I4 through a passage I5. The fluidintended to be used in the torque converter, in accordance with ordinarypractice, is oil, and hence the surfaces I3a, I31), I30, and I3d areproperly lubricated. A fluid passage I6 is provided in the intermediateshaft I2, being formed by a, plug-like member TI, and this passage is incommunication with the annular cavity 52 in the outer shell 59 of thefriction clutch I! for supplying fluid under pressure to the piston 53for engaging the clutch II. A fluid passage I6 is provided in the casingportion 35a and is defined by the shafts 46 and I3 and is incommunication with the annular cavity in the shell 56.01 the frictionclutch I3, providing fluid under pressure to the piston 53 for engagingthe friction clutch I8.

The illustrated transmission provides three speeds in forward drive anda drive in reverse. The intermediate shaft I2'is driven in all of thesespeeds by means of the torque converter I4, and this shaft functions asa drive shaft for the planetary gearing I6 in all of the speeds. Thetorque converter I4 is of the usual hydrodynamic type and functions, asis well known, to drive its driven element 32 and its driven shaft I2 atincreased torques in low'speed ranges, and the converter functions as asimple two-element fluid coupling in higher speed ranges. The torqueconverter I4 is filled with fluid by means of the passage I4 when theconverter is driving, as will be understood. The stator 33 functions tochange the direction of the flow of fluid within Y the converter, andthis element functions as a reaction element, being held stationary bythe one-way brake 36 in torque converting ranges, and the stator rotatesalong with the impeller and rotor when the converter functions as asimple fluid coupling, with the one-way brake 36 overrunning.

The torque converter is driven by means of the planetary speed-upgearing I 5. In starting a vehicle in which the transmission isinstalled, the shafts II, I2 and I3 are stationary, and since the sungear 26 is splinedto the shaft I2,it also is stationary, and rotation ofthe ring gear 21 by means of the shaft I9 causes a rotation of thecarrier 39 and thereby the impeller 3| in the forward direction at aspeed: greater than the speed of the shaft III. This is due to the factthat the planet gear set I5 includes the dual pinions 29 and 29 and isin accordance with the operation explained more in detail in A. G.Schneider Patent No. 2,333,681.: -This causes an increased torque to betransmitted to the driven shaft I2 of the converter at lowerspeeds ofthe input shaft I0 than would otherwise be the case if this speed-upgearing were not used. After the shaft I2 and any parts driven therebybegin rotation, the speed of the impeller 3| becomes more nearly equalto the speed of the input shaft I9, and the shafts I9 and I2 and theimpeller 3I engaged condition.

the same direction due to and rotor. 32, together with the parts of the.the higher speed ranges of. the shafts I9 and I2 as a simple fluidcoupling.

When the shaft I2 is rotating, there are two paths of power flow, onebeing through the torque converter M and the other being directlythrough the planet gear set I5, as is described more in detail in theabovementioned Schneider patent.

A neutral condition in the transmission is provided when both of theclutches I1 and I8 and both of the brakes l9 and are disengaged. Aneutral condition is also provided if only one of the four engageableelements is engaged while keeping the other engageable elements in dis-This is due to the fact that engagement of at least two of theengageable elements is necessary for a power train to be completedbetween the shafts l2 and II, as will be hereinafter described.

Low speed forward drive is provided by engagement of the clutch I1 andthe brake 20, with the clutch I8 and brake I9 being disengaged. Theclutch II being engaged connects the shaft l2 with the intermediateshaft I3 and thereby with the sun gear 4|. The brakeZO is engaged andthereby holds the planet gear carrier 44 ,of the gear set I6 stationary,and the gear carrier functions as the reaction element of the gear set.Rotation of the sun gear 4| in the forward direction from the driveshaft l'2 causes a rotation of the ring gear 39 and thereby the outputshaft II in the forward direction at a decreased speed. The sun gear Mand the, ring gear 39 rotate in the fact that the dual planet gear'pinions are provided between these ears.

' Second or intermediate speed forward drive is provided by'disengagingbrake 20 and engaging brake l9. The brake [9 functions to hold the sungear acting on the planet gear portion 42a. stationary, and the sun gearthereafter functions as thereaction member of the gear set. Rotation ofthe sun gear 4| from the drive shaft I2 functions to drive the ring gear39 in the forward direction at a speed faster than that speed providedwhen the brake 20 is engaged and the planet gear carrier 44 incidentallyrotates forwardly at some reduced speed.

Third speed forward or direct drive is provided by disengaging the brakeI9 and engaging the friction clutch H3. The friction clutch I8, whenengaged, functions to connect the larger sun gear 45 through the outerand inner shells 56 and 51 of the clutch l8, the bridging member 6| andthe outer shell of the clutch H with the drive shaft I2. The clutch I1,remaining engaged, connects the sun gear. 4| with the drive shaft l2, ashas been described. Therefore, with both the clutches I1 and I8 beingengaged, both sun gears 45 and 4| are connected to the drive shaft I2and the planet gear set is thereby put into locked-up condition in whichnone of the parts of the gear set rotates relative to the others, and adirect one-to-one drive is provided between shafts l2 and H.

Reverse drive is provided by engaging the clutch l8 and the brake 2|],with the clutch I1 and the brake l9 being disengaged. The shaft l2 bymeans of the clutch It drives the sun ear 45, and the brake 20 beingengaged, the planet gear carrier 44 functions as the reaction element ofthe gear set I6. Only the planet gear pinion 42 with ,its portion 42a iseffective between the sun gear 45'and the ring gear 39, and, therefore,the ring gear 39 and the shaft I connected therewith are rotated in thereverse direction at a reduced speed ratio.

The input shaft l0 and thereby an engine (not shown) connected therewithmay be rotated in the forward direction, as for starting the engine, byconditioning the gear set It for any on of its forward speed drives anddriving the output shaft I, as by pushing or towing the vehicle in whichthe transmission is installed. In this case the drive is not through thetorque converter M from the shaft I2 to the shaft Ill, but ratherproceeds through the planet gear set l5 and the one-way clutch 13. Theplanet gear carrier 30 being con- .nected through this clutch with theshaft. I2,

and the sun gear 26 of this gear set also being connected with thisshaft, cause a locking up of the gear set so that for this direction ofdrive from the output shaft H to the input shaft ID, the shafts I2 andII! rotate together in a one-toone drive. It is, therefore, notnecessary to drive the shaft I9 and an engine connected therewith forstarting purposes through the hydraulic device 14 which inherently hassomeslip between its driving and driven elements.

The illustrated transmission advantageously provides three forwardgeared speeds in series with a fluid torque converter. All of thesespeeds are two-way, that is, the drive shaft |2 not only drives theoutput shaft II at these three speeds, but, when the transmission isconditioned for any of them, the output shaft drives the drive shaft andthereby the input shaft I converter also at these speed ratios. Anautomotive vehicle with this transmission may thus utilize the engine ofthe vehicle as a braking means in any of the three speeds. Each of thethree speeds, furthermore, is completed by friction devices which allowa smooth shifting from one speed ratio to another or from neutral to anyof the speed ratios. The gear box is advantageously simpl in design,utilizing only one gear set, namely, the planetary gearing I6. It willbe noted that for direct drive, in which the transmission is used mostof the time, the two friction clutches H and I8 are both engaged, andthere is thus a minimum of power loss in these friction clutches. Thetransmission, as a whole, has a minimum number of control elements.namely, only the two friction clutches and the two friction brakes, andthis simplicity works for economy of manufacture.

I wish it to be understood that my invention is not to be limited to thespecific constructions and arrangements shown and described except onlyinsofar as the claims may be so limited, as it will be apparent to thoseskilled in the art that changes may be made without departing from theprinciples of the invention.

Iclaim:

1. In a transmission, the combination of a drive shaft, a driven shaft,a planetary gear set having first and second driving elements and athird driven element, said third element being connected to said drivenshaft, means for completing a one to one drive power train between saidshafts and including a first clutch for connecting said first elementwith said drive shaft and a second clutch for connecting said secondelement with said drive shaft which complete the one to one power trainwhen both are engaged, inner and outer concentric shafts connectedrespectively with said first and second 9 through the elements, each ofsaid clutches comprising an inner cylindrical part and an outercylindrical part, the inner part of each clutch having a plurality ofclutch discs fastened to item its outer periphery and the outer part ofeach clutch having a plurality of clutch discs fastened to it on itsinner periphery and interleaved with the first named clutch discs forfrictional engagement therewith to connect the inner and outer parts ofthe clutch together, the outer part of said first clutch being connectedto the inner part of said second clutch and to said drive shaft, theinner part of said first clutch being connected to said inner concentricshaft and thereby to said first driving element and the outer part ofsaid second clutch being connected to said outer concentric shaft andthereby to said second driving element, and means for completing achange speed drive between said drive and driven shafts including abrake for said second driving element, and said first clutch, said firstclutch and brake completing the change speed power train when both areengaged, the outer peripheral surface of the outer part of said secondclutch defining a smooth cylindrical brake drum, and said brakecomprising a friction band engageable with the outer peripheral surfacof said drum.

2. In a transmission, the combination of a drive shaft, a driven shaft,a planetary gear set having first and second sun gears and a ring gearwhich is connected with said driven shaft, means for completing a onetoone drive power train between said shafts and including a first clutchfor connecting said first sun gear with said drive shaft and a secondclutch for connectin said second sun gear with said drive shaft whichwhen both are engaged complete the one to one power train, inner andouter concentric shafts connected with said first and second sun gearsrespectively, said clutch-es each comprising an inner cylindrical shelland an outer cylindrical shell, the

inner shell of each clutch having a plurality of clutch discs fastenedto it on its outer periphery and the outer shell of each clutch having aplurality of clutch discs fastened to it on its inner periphery andinterleaved with the first named clutch discs for frictional engagementtherewith to connect the inner and-outer shells of theclutch together,the outer shell of said first clutch being connected to the inner shellof said second clutch and to said drive shaft, th inner shell of saidfirst clutch being connected. to said'inn'er concentric shaft'a-ndthereby to said'first .sun gear and the outer shell of said secondclutch'being connected to said: outer concentric shaft, and thereby tosaid second sun gear, means. for completing a change speed power. trainbetween said drive and driven shafts including said first'clutch and abrake for said second sun gear, said first clutch and said brakecompleting the, change speed power train when 'both areengaged; theouter peripheral surface of the outershell of said second clutchdefining a smooth cylindricalibrake drum, and said brake comprising afriction band engageable with the. outerp riph l rf c said drum, andhydraulic means including a fluid pressure actuated piston ,for engaginge'achof said clutches.

- DONALD W. KELBEL REFERENCES CITED 7 UNITED 's'rA'rEs PATENTS Number vI Name Date 7 752,953 Brush ;Feb. 23, 1904 1,814,297 Backer July ,14,1931 2,034,988 Nils'son Mar. 24, 1936 2,150,950 Thoma Mar. 21,19392,220,174 Ravigneaux 1 Nov. ,5,Il9 i0 2,235,370 Jandasek Mar. 18,19412,333,680 Schneider 1 ;'nov..9, 1943 2,333,681 Schneider f 'Nov. 91,19432,351,213 James "'Jun'e' 13',"1 '944 2,421,190 Dodge May 27,19479,436,071 1vIatu1aitis Feb. I7, 1948 FOREIGN PATENTS Number Country Date9,489 Great Britain- May 1 '1908 154,694- Great Britain NOVJ'30, 192048,019 France 1 Oct; 16; 1937 (AdditiontoNoL"809,102)

